Self-regulating continuosly variable transmission

ABSTRACT

A flexible mechanical linkage between two rotating shafts which allows one, the torque output shaft, to rotate at an angular velocity equal to, or variably lesser than the other, the torque input shaft. Such devices are commonly referred to as continuously variable transmissions. In this invention, a limited range of loads greater than torque input inherently cause the output shaft to rotate at a lesser velocity than the input shaft. This difference in velocities between the two shafts is proportional to the ratio of load over torque input and causes this device to adjust operation to compensate for the ratio of load over torque input. All component movements are rotational so that all mass movements are fully counter-balanced by the mass movements of other components and friction between components is eliminated by ring type roller or ball bearings. All components are well supported to withstand high torsional loads. This invention is simple, inexpensive to manufacture, compact, lightweight, offers a wide range of torque multiplication ratios, and in automotive applications, transmits engine-braking force.

BACKGROUND

Currently, in automotive propulsion systems and some stationaryapplications where fluctuating loads are encountered, torquetransmission systems with a limited number of torque multiplicationratios are used. An operator or control mechanism must select theappropriate torque multiplication ratio to compensate for any differencebetween available torque and load conditions. Also, the number of torquemultiplication ratios are limited, thus the engine providing torque mustoperate over a wide range of load conditions and rotational velocities.This adversely affects engine efficiency as most power generatingsystems operate most efficiently in a narrow range of load conditionsand rotational velocities. Operator or control mechanism input is alsorequired to select the proper torque multiplication ratio for changingload conditions.

While numerous continuously variable transmissions have been invented,including at least one self-regulating type, all have some seriousdrawback such as the generation of vibration or excessive friction orthe lack of structural strength and are thus limited in the amount oftorque that can be transmitted.

FIG. 1

FIG. 1 is a simple “skeleton” drawing in which the various componentsare represented by lines or circles. The viewer's line of sight isparallel to the rotational or orbital axes of all components.

The two different torque transmission movements are represented bysemi-circles composed of dashes with an arrow head at one point in saidsemi-circle which represents the angular direction of travel.

The juncture between the various moving components and thus the bearingswhich form the rotational axes of said components are represented bysolid dots.

FIG. 2

In FIG. 2 the viewer's line of sight is at a right angle relative to therotational or orbital axes of all components.

All shaded components are cylindrical with the viewer's line of sight ata right angle relative to the length axes of said cylinders.Illumination is from directly above, thus the bottom half of saidcylinders are in shade. The demarcation between shaded and unshadedareas represent the diameter axis centers of said cylindrical componentsand demonstrates the distance and direction of offset between saidcomponents.

The throw radii of the four crankshafts are each one eighth of one inchand the difference in diameter between the planetary gears and ringgears is one quarter of one inch.

The two bearing supports (3) which support carrier shafts (16) on outputshaft (11) are each inside one ring (12) and are thus not visible. Onesupport (3) of each carrier crankshaft (cams 17) are also inside eachring (12) and are thus not visible. The said unseen supports (3) areidentical in form and function as the visible supports (3).

With the exception of the two bearings (2) which support input shaft (4)in casing (1) and the two bearings (2) which support output shaft (11)in casing (1) all bearings (2) are inside outer components and are thusnot visible. The numbered line (2) indicates one point on the outercircumference of each bearing (2).

SUMMARY—FIG. 1 and FIG. 2

In this system two external planetary gears (15) of equal lesserdiameter drive two internal ring gears (13) of equal greater diameter byorbital and rotational movement.

Internal ring gears (13) are two hollow cylinders which have a commonoutput shaft (11) which forms the rotational axis (B) and diameter axiscenter of gears (13). Each said cylinder has an internal ring gear (13)on the inner circumference which is intermeshed with one said externalplanetary gear (15).

During direct drive, when the torque exerted into planetary gears (15)equals the load opposing ring gear (13) rotation, planetary gears (15)orbit and rotate around axis (B) in the angular direction of torqueinput (X) at torque input velocity driving ring gears (13) at torqueinput velocity. Loads greater than torque input (X) inherently causering gears (13) to rotate at a lesser velocity than torque input (X) andsaid difference in velocity is proportional to the ratio of load overtorque input.

To compensate for said difference in velocity, planetary gears (15)counter-rotate in the opposite angular direction of torque input (X) andsaid counter-rotation combines with torque input to drive planetarygears (15) in the angular direction of torque input around differentaxes.

At maximum load, planetary gears (15) counter-rotate in the oppositeangular direction of torque input, one revolution per one full orbit inthe angular direction of torque input (X). Thus planetary gears (15)with diameters equal to ninety percent of the diameters of ring gears(13) would compensate for ninety percent of torque input velocityleaving ten percent to drive ring gears (13). Such a system would have amaximum torque multiplication ratio of one to ten and a maximum angularvelocity reduction of ten to one.

During direct drive, both planetary gears (15) are driven in orbit androtation around output axis (B). Under maximum load, each planetary gear(15) is carried around a separate axis offset from axis (B).

Said two separate axes are provided by a carrier (shafts 16) which ismounted by bearings (2) on output shaft (11) between said two ring gears(13). Said carrier consists of two hollow shafts (16) which form asingle integral unit. The diameter axis center of each shaft (16) isoffset from the rotational axis (B) of said carrier provided by outputshaft (11). The direction of said offset of each carrier shaft (16) isdiametrically opposite the other relative to axis (B). Said carrier isfree to remain stationary on output shaft (11) or to rotate in thedirection of torque input at variable velocities up to torque input (X)velocity.

One of two carrier crankshafts (cams 17) is mounted by bearings (2) oneach carrier shaft (16). Said carrier crankshafts each consists of twothrow cams (17) which form a single integral unit. Each throw cam (17)is a short cylinder, the diameter axis center of which is offset fromthe rotational axis provided by the respective carrier shaft (16) towhich it is mounted.

The direction of said offset of each cam (17) Is diametrically oppositeto the other cam (17) relative to said rotational axis provided by shaft(16). Thus each said carrier crankshaft has two diametrically opposedthrows (17). Said carrier crankshafts are free to remain stationary oncarrier shafts (16) and travel in orbit around axis (B) (movement X)with shafts (16) or to rotate around shafts (16) (movement Y) when saidcarrier is stationary on axis (B) or a combination of said two movements(X and Y).

One length axis end of one connecting rod (10) is mounted by a bearing(2) on the circumference of one said throw cam (17) of each carriercrankshaft. One planetary gear (15) is mounted by bearing (2) on theother throw shaft (17) so that the diameter axis center of said gear(15) is offset from said cam (17). The direction of said offset isdiametrically opposite the direction of offset of said carrier shaft(16), relative to axis “B”, to which each gear (15) is mounted, by eachcarrier crankshaft (17).

Connecting rods (10) transmit torque from the input axis (A) to outputaxis (B) and torque reaction from axis (B) to axis (A).

Said two movements (X and Y) are generated by the input axis (A)assembly of components. Said assembly consists of an input crankshaftand a secondary crankshaft. Said input crankshaft consists of two inputaxis shafts (4), a throw shaft (6), two radial arms (5), which connectthe orbital throw shaft (6) with the rotational input shafts (4), andtwo counter-balances (7).

One length axis end of one input axis shaft (4) is connected to, anddriven in rotation, by a torque source, thus driving said inputcrankshaft around axis (A).

A secondary crankshaft is mounted by bearings (2) on orbital throw shaft(6) and travels in orbit around axis (A) with shaft (6). Said secondarycrankshaft is free to remain stationary on shaft (6) or tocounter-rotate around shaft (6) is the opposite angular director oftorque input (X).

Said secondary crankshaft consists of an axis shaft (8) and two throwcams (9). Axis shaft (8) is a hollow cylinder mounted by bearings (2) onthrow shaft (6) so that the length axis of said cylinder is coincentricwith the length axis of shaft (6).

Throw cams (9) are two short cylinders which are integral parts of axisshaft (8). The diameter axis center of each cam (9) is offset from therotational axis (shaft 6) of axis shaft (8). The direction of saidoffset of each cam (9) is diametrically opposite the other cam (9)relative to said rotational axis, thus said secondary crankshaft has twodiametrically opposed throws.

One length axis end of one connecting rod (10) is mounted by a bearing(2) on the circumference of each throw cam (9). Rods (10) transmittorque from throw cams (9) on input axis (A) to carrier crank throw cams(17) on output axis (B) and torque reaction from axis (B) back to axis(A).

During direct drive, when torque input equals load, carrier shafts (16)rotate around axis (B) at torque input (X) velocity carrying saidcarrier crankshafts (cams 17) in orbit and rotation around axis (B) thusdriving planetary gears (15) in orbit and rotation around axis (B)(movement X). Thus movement (X) drives ring gears (13) at torque input(X) velocity.

During movement (X), said secondary crankshaft remains stationary onthrow shaft (6) and said diameter axis centers of throw cams (9) orbitaround axis (A) generating an orbital cranking movement (X) around inputaxis (A).

Under a maximum load over torque input ratio, said carrier (shafts 16)are stationary on axis (b) and each said carrier crankshaft (cams 17)rotates around one said axis offset from axis (B) provided by eachcarrier shaft (16) (movement Y). In this mode of operation, saidsecondary crankshaft (shaft 8, cams 9) counter-rotate one fullcounter-revolution in the opposite angular direction of torque input (X)per one full orbit of said secondary crankshaft in the angular directionof torque input (X). The two throw radii of cams (9) remain parallel toa fixed plane in space and transmit torque from input axis (A) to twoseparate axes offset from axis (A) (movement Y).

Secondary crankshaft (shaft 8, cams 9) are limited to onecounter-rotation per one rotation of torque input (X) as movement (Y) isin the angular direction of torque input (X) and any greatercounter-rotation would increase the velocity and distance of stroke ofone connecting rod (10) and decrease the velocity and distance of strokeof the other rod (10) between axis (A) and (B). This would drive eachsaid carrier crankshaft (cams 17) at a different velocity which isimpossible as each said carrier crankshaft is engaged equally with asingle load.

Said throw radii of cams (9) act as the two radial arms of a lever withthrow shaft (6) being the fulcrum. Torque reaction exerted against eachcam (9) combines with torque input (X) from shaft (6) to drive the othercam (9) in the angular direction of torque input during both movements(X) and (Y). Thus a continuous feed back loop is created between inputaxis (A) and output axis (B).

The point at which torque is exerted into axis (B) is between axis (B),which acts as the fulcrum of a lever, and ring gears (13), which are theload. As axis (B) is fixed and said load is free to rotate around axis(B), load bearing ring gears (13) react to torque input by rotatingaround axis (B) at an angular velocity proportional to the load opposingring gear (13) rotation relative to the torque exerted into the radialarm of said lever formed by the radii of ring gears (13).

Specifications

The following factors are considered in the design of this invention.

Structural Strength

All moving components are supported by two bearings (2) and alltorsional loads on said components are between said bearing (2)supports. The exception being the two planetary gears (15) which areeach supported on one carrier throw cam (17) by one bearing (2). Thesupport provided by said single bearing (2) is directly aligned with thetorsional load to which each planetary gear (15) is subjected.

Mass Balancing

To prevent the generation of vibration due to asymmetric massdistribution around axis (A), the mass of all components which rotate onaxis (A) is balanced on axis (A) by counter-balances (7). The mass ofplanetary gears (15) is balanced on axis (B) by the mass of connectingrods (10) which is diametrically opposed to the mass of gears (15)relative to axis (B).

Friction

All moving components are supported by ring type roller or ball bearings(2) which generate very little friction.

Inertia

The mass of the moving components and the radius of orbit of said massaround the various axes is minimized to reduce the radius of travel ofsaid mass. This minimizes the inertia of said mass during changes inangular velocity of said moving components and thus any negative effectsaid inertia has on performance and efficiency.

Overall Mass, External Dimensions and Cost

This invention consists of ten moving components and eighteen bearingsand is light weight, compact and inexpensive to manufacture.

Specifications

While there are many methods to construct this device, the modeldescribed herein is the most ideal mechanical embodiment.

1. Stationary Casing

Said casing (1) encloses all the moving components in a lubricating oilbath and provides a stationary mount for the input shaft (4) and outputshaft (11).

2. Bearings

Said bearings (2) are ring shaped roller or ball type bearings (2) whicheliminate friction between the various moving components.

3. Bearing Supports

Said supports (3) are hollow cylinders which are integral parts of saidmoving components and each contain a bearing (2) which supports eachsaid moving component. Said supports (3) of secondary crankshaft (8, 9)carrier crankshafts (17) and carrier (16) are each detachable from thesesaid components to allow assembly of other components to thesecomponents.

4. Input Axis Shafts

Said axis shafts (4) are two short cylinders which are integral parts ofthe input crankshaft. One length axis end of each shaft (4) is supportedby a bearing (2) in one opposite end wall of casing (1). One length axisend of one shaft (4) is connected to, and driven in rotation around thecylindrical length axis (A) of shafts (4) by a torque source.

5. Radial Arms

Said arms (5) are integral parts of said input crankshaft and connectone length axis end of each rotational input shaft (4) with one lengthaxis end of the orbital throw shaft (6).

6. Throw Shaft

Said shaft (6) is an integral part of said input crankshaft. The lengthaxis of shaft (6) is parallel to the rotational and length axes (A) ofinput shafts (4) and travels in an orbit around axis (A) with inputcrankshaft rotation. Shaft (6) is composed of two pieces to allowassembly of other components to shaft (6). One piece of said secondarycrankshaft consists of one input shaft (4), one radial arm (5) and onepart of throw shaft (6). One said part of shaft (6) is a hollowcylinder. The second said part of shaft (6) is a solid cylinder whichhas a diameter equal to the inner diameter of said hollow cylinder.After assembly of said other components to said outer hollow cylinder,said solid cylinder is inserted inside said hollow cylinder to form asingle integral crankshaft.

7. Counter-Balances

Said counter-balances (6) are each an integral part of one input shaft(4) and are attached to each shaft (4) so that the mass of bothcounter-balances are diametrically opposite to radial arms (4).Counter-balances (6) are of sufficient mass and radius of orbit aroundinput axis (A) so as to generate a centrifugal force equal to thecentrifugal force generated by throw shaft (6) and components mounted onshaft (6).

8. Secondary Crank Axis Shaft

Said secondary axis shaft (8) is a hollow cylinder, each length axis endof which is supported by a bearing (2) and support (3) on throw shaft(6) and is free to counter-rotate on shaft (6).

9. Secondary Crank Throw Cams

Said secondary cams (9) are two short cylinders which are integral partsof secondary axis shaft (8). The diameter axis center of each cam (9) isoffset from the rotational axis (shaft 6) of axis shaft (8). Thedistance of said offset is equal to the throw radius of said inputcrankshaft. The direction of said offset of each cam (9) isdiametrically opposite the direction of offset of the other cam (9)relative to said rotational axis (shaft 6) of said secondary crankshaft.Thus shaft (8) and cams (9) form a crankshaft with two diametricallyopposed throws.

10. Connecting Rods

Said rods (10) are each an elongated bar. One length axis end of eachrod (10) is mounted by a bearing (2) and support (3) on thecircumference of one throw cam (9). Rods (10) transmit torque from inputaxis (A) to output axis (B).

11. Output Axis Shaft

Said output shaft (11) is a cylinder, each length axis end of which issupported by a bearing (2) in each opposite end wall of casing (1).Shaft (11) rotates on it's cylindrical length axis (B) and one lengthaxis end is connected to a load which is driven in rotation. Outputshaft (11) is composed of two pieces to allow assembly of othercomponents to shaft (11). One said piece of shaft (11) is a hollowcylinder with splines on the inner circumference. The other said pieceis a solid cylinder with spline slots on the circumference. Said solidcylinder has an outer circumference equal to the inner circumference ofsaid hollow piece and said solid piece is inserted into said hollowpiece after assembly of said other components to shaft (11).

12. Rings

Said rings (12) are two hollow cylinders which are integral parts ofoutput shaft (11) which forms the rotational axis (B) and diameter axiscenter of rings (12).

13. Internal Ring Gears

Said ring gears (13) are two internal gears, each one of which islocated on the inner circumference of each ring (12).

14. Ring Support Discs

Said discs are integral parts of output shaft (11) and support rings(12) on shaft (11).

15. External Planetary Gears

Said planetary gears (15) are two external gears, each one of which isintermeshed with one internal ring gear (13).

16. Carrier Shafts

Said shafts (16) are two hollow cylinders which form a single integralunit. One length axis end of each cylinder is joined to the other andeach length axis end of said unit is supported by bearings (2) andsupports (3) on output shaft (11) between said two ring gears (13). Thediameter axis center of each shaft (16) is offset from the rotationalaxis (B) of said shafts (16). The distance of said offset is equal tosaid throw radius of said input crankshaft or the throw radii ofsecondary throw cams (9). The direction of said offset of each shaft(16) is diametrically opposite the direction of offset of the othershaft (16) relative to output axis (B). Said carrier (16) is subject totorque input and torque reaction and rotates on axis “B” in the angulardirection of torque input over a range from zero to torque inputvelocity.

17. Carrier Crank Throw Cams

Said carrier throw cams (17) are four short cylinders which form twoseparate integral units with two cams (17) each. Each said unit ismounted by bearings (2) and supports (3) on one carrier shaft (16). Thediameter axis center of each cam (17) of each said unit is offset fromthe rotational axis (shaft 16) of each said unit. The distance of saidoffset is equal to said throw radius of said input crankshaft. Thedirection of said offset of each cam (17) of each said unit isdiametrically opposite to the direction of offset of the other cam (17)relative to the rotational axis (shaft 16) of said unit. Thus each saidunit forms a crankshaft with two diametrically opposed throws.

One length axis end of one connecting rod (10) is mounted by a bearing(2) and support (3) on the circumference of one carrier throw cam (17)of each said unit formed by two cams (17).

One planetary gear (15) is mounted by a bearing (2) on the other throwcam (17) of each said unit. The diameter axis center of each planetarygear (15) is offset from said diameter axis center of the cam (17) towhich each gear (15) is mounted. The distance of said offset is equal tothe distance of said offset of each carrier shaft (16) from axis (B).The direction of said offset of each gear (15) is diametricallyopposite, relative to axis (B), the direction of said offset of theshaft (16) to which each gear (15) is mounted by said carrier crankshaft(cams 17).

During direct drive when torque input equals load, said carrier (shafts16) rotates on axis (B) at torque input velocity in the angulardirection of torque input. Said carrier crankshafts (cams 17) orbit axis(B) with carrier shaft (16) rotation driving planetary gears in orbitand rotation around axis (B). Thus movement (X) drives internal ringgears (13) and output shaft (11) at torque input (X) velocity in theangular direction of torque input (X).

Loads greater than torque input inherently cause output shaft (11) andring gears (13) to rotate at a lesser velocity than torque input. Saiddifference in velocity is proportional to said load over torque inputratio. To compensate for said difference in velocity, said carrier(shafts 16) rotates on axis (B) at a lesser velocity than torque input(X) thus carrying said carrier crankshafts (cams 17) around axis (B) ata lesser orbital velocity than torque input (X).

Under a maximum load over torque input ratio, said carrier (shafts 16)is stationary on axis (B) and said carrier crankshaft (cams 17) orbitaround axis (B) is zero. In this mode of operation (movement Y), eachsaid carrier crankshaft (cams 17) rotates around the carrier shaft (16)to which it is mounted.

As the diameter axis center of each planetary gear (15) is offset fromthe cam (17) to which it is mounted; and said offset is diametricallyopposite to the direction of offset of the respective carrier crankshaftof said cam (17), relative to axis (B), planetary gears (15) orbitaround axis (B) during both movements (X and Y).

During movement (Y), the diameter axes of planetary gears (15) remainparallel to a fixed plane in space while each gear (15) is carriedaround an axis offset from axis (B). This is the equivalent of planetarygears (15) counter-rotating in the opposite angular direction of torqueinput (X) one full counter-revolution per one full orbit of planetarygears (15) around axis (B) in the angular direction of torque input (X).of ring gears (13) would compensate for ninety percent of torque inputvelocity. Such a system will have a maximum torque multiplication ratioof one to ten and a maximum angular velocity reduction of ten to one.

Movements (X) and (Y) are generated by said secondary crankshaft (shaft8, cams 9). During direct drive, said secondary crankshaft remainsstationary on throw shaft (6) and throw cams (9) orbit input axis (A).Under maximum load, said secondary crankshaft counter-rotates aroundthrow shaft (6) one full counter-revolution in the opposite angulardirection of torque input (X) per one full orbit of shaft (6) and saidsecondary crankshaft around axis (A). The throw radii of the twodiametrically opposed throws of cams (9) remain parallel to a fixedplane in space and transmit torque to two separate axes offset from axis(A) (movement Y). Said secondary crankshaft cannot counter-rotate morethan one counter-revolution per one orbit as to do so would increase thevelocity and distance of stroke of one connecting rod (10) between axis(A) and (B) and decrease the velocity and distance of stroke of theother connecting rod (10) between axis (B). Thus each rod (10) transmitstorque from axis (A) to axis (B) and torque reaction from axis (B) toaxis (A) and forms a continuous feed back loop.

The point at which torque is exerted into the axis (B) assembly ofcomponents is between axis (B) and ring gears (13). Axis (B) acts as afulcrum of a lever with ring gears (13) being the load and the radii ofgears (13) being the radial arm of said lever. Said radii react totorque input by rotating around axis (B) at an angular velocity equal totorque input relative to the load opposing ring gear (13) rotationaround axis (B).

Alternate Method of Construction

Same as described except that one planetary gear and one ring gear isused.

Said internal ring gear is a hollow cylinder with an internal ring gearon the inner circumference and an output axis shaft which forms thediameter axis center and rotational axis of said cylindrical ring gear.

Said external planetary gear is intermeshed with said ring gear andconsists of a gear, a hollow cylindrical shaft which forms the diameteraxis center of said planetary gear and two throw cams. The diameter axiscenter of each said throw cam is offset from the diameter axis center ofsaid hollow shaft. The direction of said offset of each throw cam isdiametrically opposite the direction of offset of the other throw camrelative to the diameter axis center of said hollow shaft.

One length axis end of one connecting rod is mounted by a bearing andbearing support on the circumference of each said planetary gear throwcam.

A carrier is mounted by bearings and bearing supports on said outputaxis shaft. Said carrier consists of two hollow cylindrical shafts whichform a single unit. Each said carrier shaft is offset from therotational axis of said carrier (said output axis shaft) and provides arotational axis offset from said output shaft. Each said offset axis isdiametrically opposite the other relative to said output axis.

Each length axis end of said planetary gear hollow shaft is supported onone carrier shaft by a carrier crankshaft. Each said carrier crankshaftis a short hollow cylindrical shaft, each length axis end of which issupported by a bearing and bearing support on one of the two saidcarrier shafts. The diameter axis center of each said cylindricalcrankshaft is offset from the rotational axis of said bearings whichsupport it on said carrier shaft so that said diameter axis centertravels in orbit around said carrier shaft during carrier crankshaftrotation on said carrier shaft. Said offset is equal in distance to thethrow radius of the input crankshaft.

As described, during direct drive, said carrier rotates around saidoutput shaft axis carrying said planetary gear in orbit and rotationaround said output axis.

Under maximum load, said carrier is stationary on said output shaft andeach said carrier crankshaft rotates around the respective carrier shaftto which it is mounted carrying said planetary gear in orbit around twoseparate axes offset from said output axis.

One counter-balance is attached to one bearing support of each saidcarrier crankshaft so that the mass of said counter-balance isdiametrically opposite to the direction of said offset of said carriercrankshaft offset shaft relative to the rotational axis of said carriercrankshaft.

Said two counter-balances are of sufficient mass and radius of orbit soas to generate a centrifugal force equal to the centrifugal forcegenerated by said planetary gear, connecting rod ends and throw camswhich orbit or rotate on axis (B).

Alternate Method of Construction

Said alternate method of construction is the same as described exceptthat two lesser diameter external planetary gears intermesh with alarger diameter external central sun gear. The rotational axes of saidtwo planetary gears, is parallel to the rotational axis of said centralsun gear and output shaft. Said planetary gears drive said sun geararound the output shaft diameter center of said sun gear by twodifferent rotational movements or a combination of said movements.

During direct drive, said planetary gears orbit and rotate around saidsun gear output shaft diameter center at torque input velocity. Duringmaximum torque multiplication, each said planetary gear rotates aroundeach diameter center of the gear shaft which forms the rotational axisof each said planetary gear, at torque input velocity. Planetary gearswith a diameter equal to ninety percent of the diameter of said centralsun gear would have a maximum torque multiplication ratio of one to tenand a maximum output shaft angular velocity reduction of ten to one.

Said planetary gears are supported on said output shaft by two gearcarriers. Said carriers are two elongated bars, which are mounted bybearings on said output shaft, one on each side of said central sungear. The mid-length axis center of each said carrier is mounted on saidoutput shaft so that the length axis ends of both said carriers orbitaround said output shaft. Both said planetary gears are supported bysaid carriers so that each length axis end of each rotational axis shaftof both said planetary gear are supported by a bearing located in eachlength axis end of each said carrier.

One of two connecting rods is mounted by a bearing on each said throwcam so that the inner circumference of the end ring of said connectingrod is supported by a bearing on the circumference of said throw cam.Said throw cam drives the length axis of said connecting rod in rotationaround said output shaft axis center during direct drive when saidtertiary carrier crankshafts orbit around said output shaft axis or;each said throw cam drives each said connecting rod length axis inrotation around said diameter center of one said tertiary crankshaftcarrier during maximum torque multiplication.

Each said rotational axis shaft of said planetary gears contains acrankshaft with a single throw cam or throw shaft offset from said axisshaft. Said crankshaft is located on one length axis end of each saidrotational axis shaft, on opposite ends. The throw radius of both saidcrankshafts is equal to one half said throw radius of said input throwcam or one half said distance of offset of said diameter centers of saidtertiary carrier crankshaft from said output shaft rotational axiscenter. Thus, one hundred and eighty degrees of said planetary gearcrankshaft rotation would create a linear stroke equal in length to saiddistance of offset of said tertiary carrier crankshaft diameter centerfrom said output shaft diameter center. Thus, said planetary gears arelimited to one rotation around each individual planetary gear rotationalaxis per one planetary gear orbit around said output shaft.

1. A torque transmission system in which the ratio of load relative totorque input creates an equal torque multiplication ratio. Therotational and orbital axes of all components are parallel. Said systemconsists of an input crankshaft. Said input crankshaft consists of aninput shaft. Said input shaft is driven in rotation by a torque source.Said input crankshaft also consists of a throw shaft. Said throw shaftis connected to said input shaft by at least one radial arm. Said throwshaft travels in orbit around said input shaft. A secondary crankshaftis connected by at least one bearing to said throw shaft. Said throwshaft is the rotational axis of said secondary crankshaft. Saidsecondary crankshaft consists of two throws. Each said secondary throwis offset from said throw shaft. The direction of said offset of eachsaid secondary throw is diametrically opposite the other relative tosaid throw shaft. Said secondary crankshaft is free to rotate aroundsaid throw shaft axis. The direction of said rotation is in the oppositeangular direction of torque input. The range of said rotation is fromzero to one full rotation per one full orbit of said throw shaft. Saidsecondary crankshaft divides torque input into two separate transmissionmovements. Torque reaction from each said movement combines with saidthrow shaft orbit. Said combined movement creates two separate angularmovements. Said two angular movements each occur around a separate axis.The angular direction of said separate movements is in the direction oftorque input. One connecting rod is connected by a bearing to each saidsecondary throw. Said two connecting rods transmit torque from saidsecondary crankshaft to the output assembly of components. Said rodstransmit torque reaction from said output assembly to said secondarycrankshaft. Said output assembly consists of an output shaft. Saidoutput shaft drives a rotationally driven load. Said output assemblyalso consists of at least one internal ring gear. Said output shaft isan integral part of said ring gear. Said output shaft is the rotationalaxis of said ring gear. At least one external planetary gear isintermeshed with said ring gear. Said planetary gear is of a lesserdiameter than said ring gear. Said planetary gear travels in orbit androtation around said output shaft axis. Said orbit is in the angulardirection of torque input. The angular velocity of said orbit equalstorque input. The angular direction of said rotation is in the directionof torque input. The angular velocity of said rotation is variable. Therange of said rotational velocity is from zero to torque input velocity.The maximum torque multiplication ratio is proportional to thedifference in diameters between said ring and planetary gears. Saidoutput assembly also consists of at least one carrier. Said carrier isconnected by at least one bearing to said output shaft. Said carrier isfree to remain stationary on said output shaft axis. Said carrier isalso free to rotate on said output shaft axis. The angular direction ofsaid carrier rotation is in the direction of torque input. The range ofsaid carrier rotational velocity is from zero to torque input velocity.Said carrier consists of two carrier crankshaft axis. Each saidcrankshaft axis is offset from said output shaft axis. The direction ofsaid offset of each said crankshaft axis is diametrically opposite theother relative to said output shaft axis. One carrier crankshaft isconnected by at least one bearing to each said carrier crankshaft axis.Each said carrier crankshaft consists of at least one throw. Saidcarrier crankshafts are free to orbit around said output shaft axis. Theangular direction of said carrier crankshaft orbit is in the directionof torque input. The range of angular velocity of said carriercrankshaft orbit is from zero to torque input velocity. Each saidcarrier crankshaft is also free to rotate around one said carriercrankshaft axis. The angular direction of said carrier crankshaftrotation is in the direction of torque input. The range of velocity ofsaid secondary crankshaft rotation is from zero to torque inputvelocity. One said connecting rod is connected by a bearing to each saidcarrier crankshaft throw. Said two connecting rods drive said carriercrankshaft throws. Said planetary gear is connected by a bearing to eachsaid carrier crankshaft throw. Said planetary gear is carried in orbitand rotation around said output shaft axis. Said planetary gear iscarried in orbit only around said output shaft axis by said carriercrankshaft throws.
 2. Same as described in claim 1 except: Each saidconnecting rod is connected by a bearing to said planetary gear.
 3. Sameas in claim 1 except: Said ring gear is an external gear. Said planetarygear is carried in said orbit by at least one carrier. Said carrier isconnected to said output shaft by a bearing. The direction of saidplanetary gear orbit is in the angular direction of torque input. Theangular velocity of said planetary gear orbit equals torque inputvelocity. Said planetary gear is of lesser diameter than said ring gear.The maximum torque multiplication ratio is proportion to said differencein diameter between said ring and planetary gears. Said planetary gearconsists of an axis shaft. Said axis shaft is the rotational axis ofsaid planetary gear. Said planetary gear axis shaft is connected to saidcarrier by a bearing. Said planetary gear is free to remain stationaryrelative to said carrier. Said planetary gear is free to rotate aroundsaid planetary gear axis shaft. The direction of said planetary gearrotation is in the angular direction of torque input. The range ofangular velocity of said planetary gear rotation is from zero to torqueinput velocity. One crankshaft is an integral part of each end of saidplanetary gear axis shaft. Each said crankshaft consists of one throw.Each said throw is offset from said planetary gear axis shaft. Thedirection of said offset of each said throw is diametrically oppositethe other relative to said axis shaft. Said carriers are free to remainstationary on said output shaft. Two carriers are mounted on said outputshaft by bearings. Each said carrier provides a rotational axis for onecarrier crankshaft. Said carriers are free to rotate at variablevelocities on said output shaft. The angular direction of said carrierrotation is in the direction of torque input. The range of angularvelocity of said carrier rotation is from zero to torque input velocity.Each said carrier crankshaft axis is offset from said output shaft. Thedirection of said offset of each carrier crankshaft axis isdiametrically opposite the other relative to said output shaft. Saidcarrier crankshafts each consist of at least one throw. One saidconnecting rod is connected by a bearing to each said carrier crankshaftthrow. Said connecting rods drive said carrier crankshaft throws. Saidcarrier crankshafts are free to remain stationary on said carriers andorbit said output shaft. Said carrier crankshafts are free to rotatearound said carrier axis offset from said output shaft. The angulardirection of said carrier crankshaft rotation is in the angulardirection of torque input. One secondary connecting rod is connected bya bearing to each said carrier crankshaft throw. Each said secondaryconnecting rod is also connected by a bearing to one said planetary gearaxis crankshaft. Said secondary connecting rods transmit torque fromsaid carrier crankshafts to said planetary gear axis crankshafts. Saidsecondary connecting rods transmit torque reaction from said planetarygear axis to each said carrier axis. Said secondary connecting rodsdrive said planetary gear in said orbit around said output shaft. Onehundred and eighty degrees of said planetary gear crankshaft creates alinear stroke. The length of said stroke is equal to the distance ofsaid offset of said carrier from said output shaft axis. Said planetarygear is limited to one full rotation around said planetary gear axis perone full orbit around said output shaft.
 4. Any self-regulating torquetransmission system substantially similar to the embodiment described inclaim
 1. Said system consists of one input crankshaft, one secondarycrankshaft, two connecting rods, one carrier and two carriercrankshafts. Said system also consists of at least one planetary gear oflesser diameter intermeshed with a ring gear of greater diameter. Saidplanetary gear drives said ring gear by two different rotary movementsor a combination of said two movements.